Vane type hydraulic transmission



Jan. 1, .1952

RfH. CARSON VANE TYPE HYDRAULIC TRANSMISSION 4 Sheets-Sheet 1 Filed Aug. 16, 1947 INVENTOR.

Jan. 1, 1952 R. H. CARSON VANE TYPE HYDRAULIC TRANSMISSION 4 Sheets-Sheet 2 Filed Aug. 16, 194'? ZINVENTOR.

Fo Mac 05502776395.

R. H. CARSON I VANE TYPE HYDRAULIC TRANSMISSION Jan. 1, 1952 Filed Aug. 16, 1947 4 Sheets-Sheet 3 Er v Q IN VEN TOR.

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Jan. 1, 1952 R. H. CARS N 2,581,172

VANE TYPE HYDRAULIC TRANSMISSION Filed Aug. 16, 1947 4 SheetsSheet 4 maid az fozwgys.

Patented Jan. 1, 1952 rRober-LH. @Carson, NiagaraiFaiLwN. :1'.,.; assignor .to Chisholm-Ryder Company, Jncorporated, ZNiagara;Fa1ls;N.TI.,.a icorp oration .of. N ewfYork hpplication flmst 1:6, 1947, Sel'la1 NO. 168,953

QCIaims. 4:1

.This: invention relates; to athydraulicstransmission whereby varying J ratesuof =speed-.;canlabe tobtained between the drivingtand driven shafts of any mechanism, :and more-particularly :to :;such a -t1'=ansmission which Lean he used the .drivre forlheavy dutygplant machinery.

.Qneoi thegprincipalobjects ofthe inventioniis to, providewsuch:aeheavyduty"transmission :which is-.capable oftransmitting heav loads without substantial slippage :or ,lpower .loss :and :can :be regulated to ;provide desired aoutput speed.

:Anotherobject.- is to provide such .a retransmission 'which .-is every sensitive-in. its :regulation of its output speed andlin which :such .-;reg-u-1ation can be effected with-lease.

.-Another=. object is. to zprovidezsuch a; heavy: duty hydraulic transmission which. is :.of simple construction and which -will 1: stand up under conditions orisevere and constant .use without getting out of order-.01 requiring vrepairs.

:Another object is", to provide such a hydraulic transmission inwhich ;.provision is-zmade;forzcompensating for the :expansion. and 1 contraction-pf the --working fluid. due to temperature changes.

:Another object .is to. provide suchia A transmission-which is very compact in;zproportion to the power it is capable of transmitting.

Anothereaim is TtOiDIOVid6 SHChdfi transmission iii-which; all bearinglloads, part-stressesland pressures are well within safe limits.

eAnother purpose .is to .provide '.a simple and reliable form .of governor.ior...maintalning a: constant. output speed at anysetting thereof.

Another objectistmprovide such a transmission whichis readily assembled and disassembled and which requires a, minimum .amount .of machining' toproduce the va-riousparts'of' theitransmission.

Anotherobj ect is 'to provide such a transmission in which thereis littledanger of leakage of the working liquid.

Another obiecti istto-providea hydraulic transmission, including '.-a;:;pump rotating :in raibody of liquidin-axcasing and, connecting the input and output shaftsof the ;transmission..inavwhich.

all radial and axial.forcesdeveloped withinthe pump are resisted .by .apairof bearings within said pump thereby to avoid the. necessity of .large bearings between .the shafts or. pumps; and the casing to resist suchiiorces.

Other objects and advantages .of .theinvention will appear from the following .description and drawings in which:

Fig. \1'is:a' top plan view of a hydraulic.transmission embodying i the present. invention.

i2 211s .amendcelevational aview thereof. -.-Fig. 3-3 is a vertical elongitudinal central section therethrough taken on-line 3-3..:Fig.- 2.

zFigsA isla fragmentary :verticalsectionalview takenton. line 4.-:4,.-Fig 6,.

, Figs" 5 -and-. 6: are avertical crossesectional views taken on 'the correspondingly .numbered .lines 7' is a ssideeelevational view of the rpump head which carries the-:operating ivanes of the transmission.

ll ligseflsiand -9-.-are sectional -vlews -takencon. the correspondingly numbered .linesiofz Fig; 7.

.r-Eig. ill-(is enlarged perspective viewof one of the vanes of the transmission.

flhe transmission is shown as housed within a ceasing I5 which .c-an be .of .any suitable .construction and :is vsshown as having a .rgenerally cylindrical lower ;part .IG which .iorms :a generally izcylindrical xchamber L8 =-and .a generally rectangular :upper rspart I 9 which 'forms a reservolr for ,the oihor other working liquid with which the :casingis; partly .filled. .The generally rectangular supper-i, part I 9 .isrshown as provided 25 withacoveranrhaving aifilling plug 2| anddrain plugs-malarial.shown: as provided-in. the .bottom of the. generally cy1-indrica1-lower- .part t6.

iThe ends sof the. rgenerally' cylindrical lower part I it are shown.asrclosedzbyrcircular end heads 23 removably secured in any suitablevmanner and eeachicarrying .an antifriction bearing ;24 and oilseal '25. .Thescasing. parts 115, 2 01 and 23' canzheiprovidedt with .aniextended or finnedexternal surface as .shown to dissipate !-the heat generated by the ;operation. "of. the transmission and to strengthen :tthese ,lpar-ts.

,A driveroninput shaftdfl is iournaled-in oneof the antifriction bearings-rzkand adrivenoriout put shaft3 I .is,;iournaled.. in (the -.other fantifriction shearing s24, ,ttheseshafts being, in .line with each other. :Within.-the..casing.tIi aipump-head 32 is fixed .to. the .driving or inputishaftjIlwthisbeingshownas;effected by.arkey;33..andesetiscrew 34. As'bestjs'hown in igsfT-B, f.the..hub3.5 of this pump head '32 .Lis relatively marrow an axl'al'idirection while its. rim 36' is comparatively thickin an axial direction. ,Also as ..shown.-in

these fiigures, ithe relatively thick rim 7.3.6 .of the pump head is radially slottedat. spaced intervals,

asrindicated at 3.8, to receive .a pluralityof vanes. 39 which workradiallyinand out of the.slotsj38' and are guidedand held thereby.

.As'fbesteshowniin Fig. 10, eachyane 39..is.pro-

vided with iparallluendqfaces L40, ithes.e. faces,

in assembled relation with the 7 pump ahead 32,

being arranged coplanar with the end faces of its thick rim 36. The radially outward face 4| of each vane 39 is rounded and the opposite or inner end of each vane is bifurcated to provide two legs 42 which straddle and fit the opposite faces of the comparatively thin hub 35 of the pump head 32. The inner corners of each of these legs 42 is preferably beveled or chamfered, as indicated at 43, to aid in lubrication and the opposing faces of the legs 42 are closely fitted to the opposite faces of the comparatively thin hub 35 to be guided thereby in the radial -move ments of the vanes in the slots 39.

To provide further guides for the vanes 39 in their radial movements, end rings or disks 44 are secured against the opposite end faces ofthe comparatively thick rim 36 of the pump head 32 in any suitable manner. Since the faces 49 of the vanes are coplanar with the opposite faces of the comparatively thick rim 36 of the pump head, it will be seen that the end rings or disks 44 act as end guides for the vanes 39 in the slots 38. Each of these rings or disks 44 is centrally apertured to receive the input shaft 39. A pair of loose rings 46 is arranged in the pair of annular chambers 48 provided within the pump head 32 between its comparatively thin hub 35 and each of the end rings or disks 44. These loose rings 46 engage the inner'extremities of the legs 42 of the vanes 39 and the opening through each of these rings is substantially greater than the diameter of the input shaft 39 which they embrace so that these loose rings 46 and vanes 39 are permitted to gyrate in eccentric relation to the axis of the input shaft 39.

The outer rounded faces 4| of the vanes 39 contact the bore of a cylinder 59 which is held between pump casing end heads 5| and 52, the pump casing end heads 5| and 52 being secured to the cylinder 59 so that these parts rotate in unison. The hub 53 of the end head 52 is fitted on the driven or output shaft 3| and abuts against a flange 54 on this shaft. This hub 43 is shown as secured to this flange by screws 55 and hence it will be seen that the pump casing or cylinder assembly 59, 5|, 52 rotates with the driven or output shaft-3|. The hub 59 0f the end head 5| of this cylinder assembly carries a bearing 58 in which the drive or input shaft 39 is journaled.

Each end ring or disk 44 is fitted into a recess provided in'the corresponding pump casing end head 5|, 52 so that these end rings 44, pump casing end heads 5|, 52, and the cylinder 59 form the working chamber 59 for the pump head 32 and its vanes 39. This cylindrical working chamber 59 is in eccentric relation to the axis of the input and output shafts 39, 3|.

An important feature of the invention resides in the provision of a pair of taper roller bearings 6| between the input shaft 39 and the pump 88.5. ing or cylinder assembly 59, 5| and 52 which is fast to the output shaft 3| as above described. These taper roller bearings 6| are in opposed relation to each other and not only. serve to resist axial thrust of the input and output shafts but also resist radial movement of these shafts relative to each other, large radial forces being created by the pressures built up within the pump connecting the ends of these shafts. To house this pair of taper roller bearings 6| each of the end heads 5|, 52 is'provided with a coaxial cylindrical recess 52 on the side of the corresponding end ring 44 opposite from the working chamber 59. Each taper roller bearing comprises an outer race 63 fitted in the corresponding cylindrical recess 62 and having an inwardly facing tapered or conical raceway, an inner race 64 fitted around the input shaft 39 and having an outwardly facing tapered or conical raceway, and a series of tapered roller bearings riding in these raceways. The tapered or conical raceways of the races of the'tw'o bearings 6| are in opposed relation so that a projection of the surfaces of companion raceways of the two bearings intersects a vertical medial plane through the pump, and hence it will be seen that they resist end thrust between the input shaft 39 and the pump casing or cylinder assembly 59, 5|, 52 in both axial. directions and since this casing or assembly is fast to the driven or output shaft 3|, it will be seen that these thrust bearings 6| resist endwise thrust of these shafts. Equally important, however, is the fact that these taper roller bearings resist radial or lateral forces. The pump develops heavy off-center pressures and hence heavy lateral or radial forces develop between the pump casing or cylinder assembly 59, 5|, 52 and the input shaft 39. These radial forces are adequately resisted by the taper roller bearings 8|. The bearings 9| between the input and output shafts are therefore built into the hydraulic transmission connecting these shafts so that external end thrust or radial bearings to resist these forces are unnecessary. The necessity for such bearings external of the transmission to resist end thrust and radial forces developed within the transmission has been one of the principal disadvantages of transmissions of this type as heretofore developed.

The working chamber 59 has an elongated inlet groove or port 68 extending circumferentially along the lower part of the working face of the cylinder 59 and has an elongated outlet groove or port 69 extending circumferentially along the' upper part of the working face of the cylinder 59. These ports extend, respectively, along the enlarging and decreasing moon-shaped parts of the working chamber 59 and which are formed by the eccentric relation of the working chamber 59 with reference to the axis of the pump head 32.

The inlet groove or port 68 is connected by a passage 19 extending through the cylinder 59 and end head 52 to an inlet opening 7| provided through the end face of this end head 52. The outlet groove or port 69 is connected by a passage |2 extending through the cylinder 59 and end head 5| to an annular chamber 13 in the hub 56 of the end head 5| and around the hearing bushing 58 therein. This hub 56 of the end head 5| is provided with an annular series of ports 14- leadingfrom the annular chamber 13 to the-cylindrical external face thereof.

On this cylindrical external face of the hub 56 is slidingly mounted a cylindrical valve sleeve 15 which is movable to cover and uncover the ports This valve sleeve l5 rock shaft 89 can be oscillated to actuate the. valve sleeve I5, by any suitable linkage, a rock atomizalever bei'ngshowmin dottedlines at 8-2 forthis: purpose? In order to-- prevent undue: churning of the working liquid contained withinthe casing: I5, a;- cup-shaped cylindrical sheet metal endhead 83- is-fitted over the end head 51-, this sheet metall end head 83- beingoentrally'apertured to fitaround the-valvesleeve 15. Asimilar cup-shaped.cylindrical-sheetmetal endhead fid isfitted-over the end head-52-, this sheet'metal end head-filbeingprovided witha central opening 85 I of sufficient size; to-permit readyflow of the Working liquid from.- thecasing l-to the-inletport-li A- feature of the inventionresides inthe provision of a simple form of governor to; maintain a. constant speed of the driven or: output shaft- 3 i regardless of the speedon the driving. or. input shaft 3i'F. For this purpose a paddle"? 88-: is: ar rangeddengthwiseofthe input: and outputzshaitsl 30% 3 l within=the upper geser allyrectangularrpanti hot the casingiei and -is hung'frompivot.pinslfih, these pivot pine-extending: coaxially: through the.- opposite end walls ofa the upper generally rec-s tangular part w'ot-the casing i5 and supporting theopposite ends on the paddle t8 neari the upper. edge thereof; A pin= fiithaving a baliz head pro jectsoutwardly fromone; side'of the paddle- 8B," ass-best shown inhi 5-, and the end of. this pin-.is connected: by'a' link: 9-l with-a similar pin- 92. pro jeetihgoutwardly from a lever armi93, as-best shown inFigs. i and ii This-lever arm: 934s fast to therock= shaft llfi and proiects upwardly there from; Themovement of the leverarmed is. limit? ed-by-a bracket fi l secumd teone side of thegene erally rectangular part id: of the casi'ng 1e and having a flange 95s projectingltowardn thelever arm 93, this flange being. provided xwitha. recess. 95 in which; the lever: amnawfi3 1 works nine-normal closedspositioniof the valvelsleeve E5- the lever arm 93 engages the left. handi extremity of: the recess 9G as viewed in Fig;-4,. this recess thereby providing ast'opfor the closing movemenhof: the sleeve valve mechanism. The movementof this sleeve valve meohanism in.- the opposite.- direction is limitedibyi the rig-ht11hand. extremity of; the recessziifi; as viewedzinlrr igzep The action of the; paddlei BBz as. agovernon is. dependent upomthe: movementiofithe liquid'in the casing t5; asiindu'cedzbyi the; rotationithe pump assembly. whichs connects theiinput or drive shaft 3th with thezoutputirorw driven shaft 3i:.. 13040110- vide a. generally:- linean' response; of the paddle to the rotation.-ofithis pumpiassembiy, izt ismdesim able-to provide:a-:.fiange:& which extends the-full: lengthtof this .paddleiandiprojectsain opposed relaticn" to the movement: or the: working liquid; this movement; being. indicated; by; the arrow shown in; Fig. 5... V

In oider. to;adj11sti the-paddle ilfiito provid'e' any desired. speed; of the: output: shaft;- 31; theepaddlev is provided; with. an; adjustable. countenweighta. For: this; purpose. an. L-shapedr bracket: 992 is: see cured tonthattsidesof thepaddlefilt oppositefrom the'flange 9'8; so asstozprovide a.horizonta1ishelf thereon. On .thiscshelf is seated: a plunger ltd which is: slidingly mounted in\ a guideway: Iii-i provided-*in -theccver 2t; as;bestshown in Fig; 3". This plunger extends exteriorly of the cover anda counterweight W2 isremovably' secured to-itsuppependa Thi's removalfisshown as effected-by 7 a' set screw H13 which secures-thecounterweight M2" to the plunger- Hit; It will beseen' that by removing the counterweight l 92 and substituting a heavier or lighter weight, movement of" the paddle 88 induced" by the working liquid within the casing willzb'ewrestrictedtoiaagneatenor less: degree and that-hence itsiaction-i'n actuatingthe? valve sleeve 115iwillibeladjustediaccordinglyl.

Operation In theoperatiomof the,-transmission, the reser voir provided by the casing: l5; i fillediwith a; working liquid-,.such' as oil; to a. point; near the cover; 2 0' theiten'fp this; filling being; efiected; by removing the: filling: plug 23:, Assuming; that: the; LEIIVEISISEVBZISEiSliILthe position shown inxFfig; 3; which it; completely covers: the: ports: 14; the; liqui'dlto be pumped by the; pump'assembly canr not: escape from; the pump. assembly? and thence; the. pump assembly connectingitheinputzandzoutaput shafted-5.; 31!; is' hydraulically'locked so; that; the driven or output shaftw isadriveneiatthezsame; speed as theinput or drive shaftw;

To manually:reducetherspeed:of the dri s/en";v or output shaft 31k to that desired, the,=le.ver 8.25. is moved in a corresponding. direction; so as; to; rock the rock shaft; 811 (Fig: 6). andswing'the; yoke79 in a corresponding direction... Thezrollers; T. at the ends oil the arms. of the-yoke 1.9; are; arranged in the groove: Hit of i the valve sleeve 15 and thismovement ofithis'lyokel moves thissvalve sleet/e75 to theleftas: viewedcin Fig; 3.. This; movement of the valve sleeve opensthepor-tsflllr through the hubvofflthezendheadii Iz to a v propontionatedegree and hence; the: working liquid: is; pumped by the pumpassembly connecting the; input and output shafts 30bit. Intthis pumping, action the working liquid from. the casing:v I15; enters the central p opening" in" thesheetmetal end head 84 and passeslnto thezinletzopening.Iii: of the end head 52; From thisl'inletopeningfll. the working liquid passesthrough theipassage ll'li into the elcngated groove or port 68 withirnthe. working chamber 59. This oil is: drawnby the, vanes 39 into the workingchamber:59:bysreason. of the eccentric relationofthiscylindrical:working chamber tothe axis. of the inputandLoutput. shafts 30','3l, thesevanes, along the inlet'groovet or port 68 providing: a series ofienlarging chambers as many conventional vane type pump. Inpassing above the center Qf thepump these-cham-- bersbetween the-vanes 39 contract and hencethe working liquid is pumpedoutthrough the elongated groove or outlet port 69 in the upper side of the working chamber From this grooveor outlet port 69 theworking liquid passes, through the passage 12' into theannular chamber 13- provided in the hub it around the bearing bushing 58 and thence escapes through the partially opened outlet port's H back into the main body' of-workingliquid-withinthe casing 15. It will be seen that-by opening these-ports l i 'through an uncovering action of the 'valve sleeve TS-a degree of slippage is provided-between-t-he drive" orinput shaft 30 and thedri'ven oroutput'shait 31 so'that a differential in their speeds is" provided; the speed of the output or driven shaft 3| being reduced. The speed of the driven. or output. shaft 3| is dependent'upon this. degree of slippagaand; hence it will be seenthat any desired reduced speed of the drivenor output shaft-3i can-be ob tained by moving the valve sleeve. l5v to uncover, the ports 14 to acorresponding degree;

In the action of the, pump assembly which con.- nects the input and output shafts 30, 3|. it: will: be seen that the vanes 39 are maintainedin' constant contactwith the working surfaces of the cylinderSl) by the pair of loose'ri'ngs ls-which engage the inner extremitiesof the legs 42- of" thesevanes; these ringsrotatingineccentricrelation to the axis of the drive or input shaft 3! and being of such size as to insure contact between the vanes and the eccentric working surface of the cylinder 50. These vanes 39 are held against endwise displacement by the disks or rings 44 and by the hub 35 of the pump head 32 which the legs 42 of these vanes straddle.

It will be particularly noted that the taper roller bearings 6| are arranged internally of the pump and serve to resist both radial and axial forces developed therein. Thus, these bearings are between the input shaft 30 and the pump casing or cylinder assembly 50, 51 and 52 fast to the driven shaft and hence resist lateral forces between this pump casing or cylinder assembly and the pump head 32 and vanes 39 carried by the input shaft. Since the pressures developed by the pump are off-center and of considerable magnitude, this action of the bearings 61 is of importance. Further, by reason of their tapered form, these bearings 6i resist axial thrust of the input and output shafts. This avoids the necessity of providing large bearings between the pump and the casing to resist such forces.

The action of the governor is as follows:

Assuming that it is desired to have a constant speed of the driven or output shaft 3i regardless of the speed of the input shaft 39, the counterweight I02 on the plunger I!) is selected to obtain this result. As long as the driven or output shaft 3! rotates, the pump assembly within the casing l5 rotates in the direction of the arrow shown in Fig. 5. This rotation of the transmission causes the working liquid within the casing to impinge against the paddle 88 and thereby swing it to the left, as viewed in Fig. 5. This movement of this paddle causes it to draw upon the link 9! and thereby rotate the lever arm 93 clockwise, as viewed in Fig. 4. This rotates the rock shaft 80 clockwise, as viewed in Fig. 3, u this moving the yoke or fork 19 fast to this rock shaft to the left, as viewed in Fig. 3, so as to uncover the ports H to a greater degree. The uncovering of the ports 14 to a greater degree thereby increases the degree of slippa e in the transmission and causes the transmission assembly to rotate at a slower speed, the maximum speed of rotation of this transmission assembly being, of course, when the ports 14 are completely closed and the transmission hydraulically locked. In consequence of this increase in the effective opening of the ports 14, the rotation of the driven or output shaft 31 and the transmission housing fast thereto is decreased so that the action of the working liquid against the paddle B8 is reduced and the paddle 88 swings back to the position corresponding to the speed of the output shaft 3! which it is set to maintain. If a higher output speed is desired, a lighter weight )2 would be fixed to the plunger I00, and if a slighter output speed is desired this weight would be increased.

From the foregoing it will be seen that the present invention is a very simple and inexpensive heavy duty transmission and in which all thrust forces are adequately compensated. It will further be seen that the transmission has a very simple governor which serves to maintain, within very close limits, and in a very simple manner, any desired output speed of the transmission.

I claim:

1. In a transmission having a casing adapted to contain a body of working fluid, a power input shaft extending into said casing, a power output shaft extending into said casing, a pump connecting said shafts and having a part rotating with said output shaft and immersed in said working fluid and pumping said working fluid from said body of working fluid back into said body of working fluid, and a throttling valve for said pump, the combination therewith of a governor for maintaining a maximum speed of said output shaft, comprising a paddle arranged in said body of working fluid adjacent said rotating part in position to be deflected in response to the movement of said working fluid induced by the rotation of said rotating part, and means operatively connecting said paddle and throttling valve to open said throttling valve in response to increasing deflection of said paddle.

2. In a transmission having a casing adapted to contain a body of working fluid, a power input shaft extending into said casing, a power output shaft extending into said casing, a pump connecting said shafts and having a part rotating with said output shaft and immersed in said working fluid, and pumping said working fluid from said body of working fluid back into said body of working fluid, and a throttling valve for said pump, the combination therewith of a governor for maintaining a maximum speed of said output shaft, comprising a paddle pivoted in said casing with a free end arranged in said body of working fluid adjacent said rotating part in position to be deflected in response to the movement of said working fluid induced by the rotation of said rotating part, and means operatively connecting said paddle and throttling Valve to open said throttling valve in response to in-.

creasing deflection of said paddle.

3. In a transmission having a casing adapted to contain a body of working fluid, a power input shaft extending into said casing, a power output shaft extending into said casing, a pump connecting said shafts and having a part rotating with said output shaft and immersed in said working fluid and pumping said working fluid from said body of working fluid back into said body of working fluid, and a throttling valve for said pump, the combination therewith of a governor for maintaining a maximum speed of said output shaft, comprising a paddle arranged in said body of working fluid adjacent said rotating part in position to be deflected in response to the movement of said working fluid induced by the rotation of said rotating part, means operatively connecting said paddle and throttling valve to open said throttling valve in response to increasing deflection of said paddle, and adjustable means biasing said paddle to a position holding said throttling valve in a closed position.

4. In a transmission having a casing adapted to contain a body of working fluid, a power input shaft extending into said casing, a power output shaft extending into said casing, a pump connecting said shafts and having a part rotating with said output shaft and immersed in said working fluid and pumping said working fluid from said body of working fluid back into said body of working fluid, and a throttling valve for said pump, the combination therewith of a governor for maintaining a maximum speed of said output shaft, comprising a paddle pivoted in said casing with a free end arranged in said body of working fluid adjacent said rotating part in position to be deflected in response to the movement of said working fluid induced by the rotation of said rotating part, means operatively connecting said paddle and throttling valve to open said throttling valve in response to increasing deflection'iof asaid :pa'd e and adjustable means biasingsaid paddle to a position holding said throttling ,valve in a closed position, comprising a member ,oprat'ively c'onnected'with said paddle to move ,therewith anda cou'nterweight, on said member.

' 5'. In a.transmi'ssion hayingla casing adapted toicontainla body of working fluid, a power 'input shaftlextending into said teasing, a power output shaft extending intorsaidlcasing, a pump connectinglsaid shafts andchaving a part rotating with said output shaft and ,immersed-inisaid work n fluid and ,numpi. i said work n jflui from said body of working fluid back into said body of working fluid, and a throttling valve for said pump, the combination therewith of a governor for maintaining a maximum speed of said output shaft, comprising a paddle pivoted in said casing with a free end arranged in said body of working fluid adjacent said rotating part in position to be deflected in response to the movement of said working fluid induced by the rotation of said rotating part, means operatively connecting said paddle and throttling valve to open said throttling valve in response to increasing deflection of said paddle, and adjustable means biasing said paddle to a position holding said throttling valve in a closed position, comprising a vertical plunger guided by said casing and extending exteriorly thereof, a counterweight removably secured to said plunger externally of said casing, and means operatively connecting the opposite end of said plunger with said paddle to bias it to said position.

6. In a transmission having a transmission casing adapted to contain a body of working fluid, a power input shaft journaled in a wall of said casing, a power output shaft journaled in the opposite wall of said casing in coaxial relation to said input shaft, a pump casing rotating with said output shaft and having a working chamber, a pump rotor in said working chamber and rotating with said input shaft, said pump casing being provided with an inlet passage leading from said body of working fluid to said working chamber and an outlet passage leading from said working chamber back to said body of working fluid, a valve for throttling the passage of said working fluid through said passages, the combination therewith of a governor for maintaining a maximum speed of said output shaft, comprising a paddle pivoted to said casing along an axis extending generally parallel with said shafts and having its free end arranged in said body of working fluid and adjacent said pump casing to be deflected in response to the movement of said working fluid induced by the rotation of said pump casing, and means operatively connecting said paddle and throttling valve to open said throttling valve in response to increasing deflection of said paddle. I

v 7. In a transmission having a transmission casing adapted to contain a body of working fluid, a power input shaft journaled in a wall of said casing, a power output shaft journaled in the opposite wall of said casing in coaxial relation to said input shaft, a pump casing rotating with said output shaft and having a working chamber, a pump rotor in said working chamber and rotating with said input shaft, said pump casing being provided with an inlet passage leading from said body of working fluid to said working chamber and an outlet passage leading from said working chamber back to said body of working fluid, and a valve for throttling the passage of said Working fluid through {said ,zpassages, the combination P ,vsrtica ,p sit qn and adju table means biasine said paddle toward said normal ,verticalposition.

8. In a transmission having a transmission casing adapted to contain a body of working fluid, a power input shaft journaled in a wall of said casing, a power output shaft journaled in the opposite wall of said casing in coaxial relation to said input shaft, a pump casing rotating with said output shaft and having a working chamber, a pump rotor in said working chamber and rotating with said input shaft, said pump casing being provided with an inlet passage leading from said body of working fluid to said working chamber and an outlet passage leading from said working chamber back to said body of working fluid, and a valve for throttling the passage of said working fluid through said passages, the combination therewith of a governor for maintaining a maximum speed of said output shaft, comprising a paddle pivoted to said casing along an axis generally parallel with said shafts and directly above said pump casing and having a depending free end arranged in said body of working fluid and adjacent said pump casing to be deflected from a normal vertical position in response to the movement of said working fluid induced by the rotation of said pump casing, means operatively connecting said paddle and throttling valve to open said throttling valve in response to increasing deflection of said paddle from said normal vertical position and adjustable means biasing said paddle toward said normal vertical position, comprising a member projecting horizontally outward from the side of said paddle opposite from that against which said working fluid impinges, a vertical plunger having its lower end supported on said projection and extending exteriorly of said casing, and a counterweight supported by said plunger.

9. In a transmission having an input shaft and a coaxial output shaft, a pump casing fast to one of said shafts and iournaled on the other of said shafts and providing a cylindrical working chamber arran ed eccentrically with reference to the axis of said shafts and providing inlet and outlet passages leading, respectively, to oppositely located inlet and outlet grooves extending circumferentially along said working chamher, said other of said shafts extending through said working chamber, a working fluid reservoir connecting said inlet and outlet passages and means for throttling the passage of said working fluid through said passages, the combination therewith of a pump rotor fast to said other of said shafts and arranged in said working chamber, comprising a pump head having a central hub which is relatively thin in an axial direction and a centered rim which is relatively thick in an axial direction and radially slotted, a plurality of vanes in said slots each bifurcated to straddle said hub, a pair of circular disks apertured to fit said other of said shafts and fitted against opposite sides of the rim of said pump head and forming a pair of annular chambers therein, and means holding said vanes in engagement with the cylindrical working face of I said working chamber, comprising a circular, loose ring in each of said annular chambers and loosely encircling said other of said shafts to be bodily movable radially relative thereto and engaging the end of the bifurcations of said 10 vanes.

ROBERT E. CARSON.

REFERENCES CITED The. following references are of record in the file of this patent:

Number 12 UNITED STATES PATENTS Name Date Schumucker June 9, 1908 Hopkins June 13, 1933 Matthews July 30, 1935 Vincent Feb. 25, 1936 Gambrell Apr. 13, 1937 Owens Apr. 2, 1940 Cook Mar. 9, 1943 Anderson Jan. 4, 1945 Armstrong Mar. 20, 1945 Dillon' Aug. 26, 1947 Von Wangenheim Jan. 25, 1949 

